Derailleur

ABSTRACT

A derailleur  10 , for moving a chain  60  to different sized sprockets arranged small to large in a sprocket nest  101  is disclosed. The derailleur  10  has a pivot guide feed arm  11  for directing the chain  60  onto one of multiple sprockets within the sprocket nest  101 . The pivot guide feed arm  11  is rotatably mounted at a pivot end on an angular pivot pin  12  and when the pivot guide feed arm  11  rotates about the pivot pin  12  an opposite chain guide end of the pivot guide feed arm  11  traces a path substantially parallel to a tangent to the outer periphery of the sprocket nest  101 . The movement of the pivot guide feed arm  11  is mechanically driven by a user command and is preferably moved by a connected rod or wire or cable  109.

TECHNICAL FIELD

This application relates to a speed changing device for rider propelled vehicles using a chain drive and a sprocket nest with a plurality of different sized sprockets. The sprocket changing device is a pivoting derailleur system with a derailleur and a chain slack take-up mechanism.

BACKGROUND OF THE INVENTION

The derailleur system currently used in bicycles has been adequately engineered to allow the chain to smoothly move to an adjacent sprocket at selected locations around each sprocket. Each sprocket is modified to provide clearance for chain shifting with a small plurality of reduced size chain pickup teeth with modified shape at selected locations on the sprocket, but with adjacent normally sized teeth providing adequate chain grip and strength around the rest of the sprocket's outer periphery or circumference.

The chain travel is directed by a movement of the derailleur guiding the chain from the sprocket it is on and feeding the chain onto an adjacent larger sprocket when decreasing the speed or a smaller sprocket when increasing the speed.

The bicycle derailleur devices are physically mounted on the frame of the bicycle and its movement is generally operated by a guide wire or cable extending from a shifting lever attached on the handle bar to the derailleur. When the rider selects a new sprocket, he moves the lever moving the wire or cable which in turn repositions the derailleur to effect a sprocket change. The derailleur is a sophisticated device that has a fixed structure attached to the frame or rear axle and a movable structure that is held in position by at least one double pivot with multiple heavy duty springs that allow the movable elements to rotate or move in the path of a parallelogram created by two opposing plates hinged to move parallel relative to the other. This movement enables the chain guide portion of the derailleur to move relative to the sprocket nest in a relatively uniform path in relation to the guide and the sprockets while minimizing twisting the chain.

In order to function properly, the chain slack that exists when the chain is on the sprocket must be taken up. The amount of chain slack is reduced as the chain moves to larger sprockets. In bicycles, the derailleur chain guide system is positioned to extend well below the axle and frame. This enables the chain to serpentine through the low hanging derailleur guide system by having the chain extend well below the largest of the sprockets.

These prior art derailleur devices allow the chain to be moved along the various sized sprockets with relative ease.

In U.S. Pat. No. 7,780,558 entitled “Bicycle Rear Derailleur” assigned to Shimano Inc.; a rather detailed description is provided of these rather sophisticated devices for changing sprockets on a bicycle. Shimano is a world leader in the manufacture of derailleurs and is known for providing some of the best devices for changing sprockets on chain driven bicycles. Their rear derailleurs are engineering marvels exhibiting good reliability and durability.

These excellent products, however, because they are so well made with much sophistication are costly. A need exists to provide a simpler, less complex derailleur design that is reliable and durable.

Recently, a new generation of scooters and bicycles has been developed with reciprocating foot pedals. These vehicles, particularly the scooters, have frames that have a very low center of gravity to make the vehicles more stable. The frames are so low to the ground that the prior art derailleurs conventionally positioned below the rear sprocket nest are virtually useless. Nevertheless, these vehicles need a shifting device to allow the rider to selectively change speeds.

It is therefore an objective of the present invention to provide a derailleur type device and chain slack take-up assembly that does not extend into the ground clearance of the vehicle. It was a further objective of the present invention to provide a reliable and less complex device that can be manufactured at an affordable cost.

It was still another objective of the present invention to provide a derailleur device with a large range of motion to facilitate the range of rear sprocket sizes in a single rear sprocket nest equivalent to present bicycle derailleurs.

Another objective of the invention is to have the chain feed to the derailleur chain take-up directed so as to be fed close to the centerline of the drive sprocket.

These and other features of the derailleur system of the present invention are described as follows.

SUMMARY OF THE INVENTION

A derailleur, for moving a chain to different sized sprockets arranged small to large in a sprocket nest is disclosed. The derailleur has a feed arm for directing the chain onto one of multiple sprockets within the sprocket nest. The feed arm is rotatably mounted at a pivot end on a single angular pivot and when the feed arm rotates on the pivot an opposite chain guide end of the feed arm traces a path substantially parallel to a tangent to the outer periphery of the sprocket nest. The movement of the feed arm is mechanically driven by a user command and is preferably moved by a connected rod, wire or cable. The guide end of the derailleur has a chain guide, wherein the chain guide can be a smooth surface or a roller or toothed roller. The derailleur further has a chain slack take-up assembly having a pivotal take-up idler arm for chain slack take-up, which is pivotably connected to the chain guide end of the feed arm. Preferably, the feed arm and the pivotal take-up idler arm share a chain guide wherein the feed arm and idler arm are both spring loaded, preferably sharing the same spring wherein one spring biases both the feed arm and idler arm, the spring being connected to the idler arm and onto the angular pivoting feed arm.

One end of the spring is connected to the pivot guide feed arm at or near the frame pivot, the opposite end of the spring is connected to the chain slack take-up idler arm on a pivot pin eccentric to the pivot biasing the chain slack take-up idler arm providing the chain slack take-up, wherein the chain pivot guide feed arm and chain slack take-up idler arm assemblies lie within a space between the driver sprocket and driven sprocket nest, the space defined as the area between the major diameter sprocket of the driver sprocket and driven sprockets.

A chain slack take-up idler arm has a pivotal idler arm for taking up chain slack, the idler arm having a pair of chain guides, one being a feed guide, the other a take-up guide, at opposite ends to serpentine the chain through the guides; and a spring, pulling the chain slack take-up idler arm to maintain chain tension; and wherein the excess chain slack is stored in the space between the driver and driven sprockets.

The chain slack take-up idler arm allows the chain to straighten when positioned on the largest sprocket pairs. The chain slack take up idler arm lies within a space between the driver sprocket and driven sprocket nest, the space defined as the area between the major diameter sprocket of the driver sprocket and driven sprockets. The chain guides are smooth surfaces or rollers with or without teeth.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 shows a side view of a bicycle with a prior art rear derailleur for a bicycle shown.

FIG. 2 is a side view of a bicycle with reciprocating pedals with the derailleur of the present invention shown in the large sprocket position.

FIG. 3 is perspective view of the derailleur assembly with a chain slack take-up assembly oriented in the large sprocket feed position.

FIGS. 3A and 3B are a top view and a side view taken from FIG. 3.

FIG. 4 is an exploded view of the derailleur assembly of FIG. 3.

FIG. 5A is a partial plan view of the chain and derailleur wherein the small rear sprocket is engaged with the chain shown in dashed lines.

FIG. 5B is the schematic view of FIG. 5A, but with the large sprocket engaged with the chain shown in dashed lines.

FIG. 6 is an alternative embodiment derailleur assembly with a hub projection to allow pivot rotation in excess of 180 degrees.

FIG. 7 is another alternative embodiment for over 180 degrees rotation of the derailleur with a lanced spring support.

FIG. 8 is a view of a top swivel connector for the spring.

FIGS. 9A, 9B and 9C are diagrammatic bottom views of the derailleur assembly showing the position of the feed chain path and the idler sprocket when the small, medium and large nest sprockets are engaged. The top portion of the chain is not shown for clarity.

FIGS. 10A, 10B and 10C are schematic views of the rear sprocket nest and front drive sprocket and the space between the sprockets in which the derailleur moves.

FIGS. 11A, 11B and 11C are diagrammatic views of the chain path similar to FIGS. 9A-9C, but with the dual drive sprocket.

DETAILED DESCRIPTION OF THE INVENTION

FIG. 1 is a side view of a prior art single derailleur assembly 202 moved by a shift mechanism 206 and guide cable 209 at the handle bar 208 used on a bicycle 200. As can be seen the device is attached to the rear wheel hub and therefore positioned well below the rear wheel sprocket nest 201. This enables the chain 204 to extend from the forward drive sprockets 203 rearwardly with the chain 204 forming two almost parallel straight lines to the rear wheel 205 sprocket nest 201 and derailleur assembly 202. The derailleur assembly 202 is shown directly under the combination of the rear sprocket nest 201 and the rear axle 207 which means the lower part of chain 204 is positioned close to the ground as shown, but well above the lowest point on the pedal 210.

The revolution of the pedals 210 is a continuous 360 degree movement with the lowest point of the pedal stroke clearing the ground by several inches, thus providing adequate ground clearance during a severe leaning turn.

With reference to FIG. 2, a reciprocating pedal bicycle 100 is illustrated. The bicycle has a low slung frame 110 with a pair of reciprocating foot pedals 102 that move up and down to provide forward propulsion. The ground clearance on both the frame and the bottom stroke of the foot pedals 102 is a mere few inches in some models. The reason for the low center of gravity is a desire to maintain superior ride stability with reduced rider's ability requirements. Those bicycles and in some versions, scooters can achieve excellent speeds which are best accomplished with the use of a gear shifting mechanism. As is readily apparent, conventional low hanging derailleur assemblies simply would drag on the ground unless the ground clearance was raised, sacrificing ride stability and the ability to design a low frame with a frame bottom adapted to ride down railings similar to techniques used in skateboarding.

To overcome this problem, an improved concept in gear shifting design was required that still utilized an existing gear shift mechanism 106 mounted on the handle bar 108 and a single shift cable 109.

As shown in FIG. 2, and in greater detail in FIG. 3, a derailleur assembly 10 with a chain slack take-up idler arm 20 is illustrated. A low-hung system such as scooters can not use a guide system that requires major clearance between the driven wheel center and ground, however, a system that utilizes the space beneath the top driving links of chain and above a line between the bottom of the largest nest sprocket 101L and the bottom of the largest forward drive sprocket 103. As illustrated, the entire derailleur assembly 10 is located between the space of the largest or major diameter rear sprocket 101L of the sprocket nest 101 and the major diameter of the forward drive sprocket 103. Accordingly, an upper line and a lower line drawn between these major diameter forward and rear sprockets is all the space needed for the chain take-up and derailleur assemblies. As shown, the derailleur assembly 10 does not occupy the ground clearance space as required in the prior art devices, but rather is packaged between the pair of major diameter sprockets. This is a significant breakthrough in gear shift mechanisms because it dramatically reduces the vertical space required for the chain. The design is useful not only in low hung vehicles, but in any bicycle. Consider how many derailleurs have been bent or broken when they hit a rock or downed tree when mountain biking. This more protected position of the derailleur assembly 10 of the present invention dramatically reduces this type of risk.

As shown in FIGS. 3, 3A, 3B and 4, the basic element of the derailleur assembly is a pivot guide feed arm 11 located on a pivot pin 12 fixed to the frame 110 or otherwise affixed to a bracket for mounting onto the frame 110 at an angle relative to the change sprocket assembly or rear sprocket nest 101. The upper end of the pivot guide feed arm 11 supports a guide roller 30 as well as the upper end of the chain slack take-up idler arm 20 with a take-up roller 40 at the bottom opposite end of the chain slack take-up idler arm 20. The pivot pin 12 being at an angle tends to promote chain twist, but the sprockets themselves limit that motion to allow smooth change of position. Each of the roller sprockets 30 and 40 as shown has a small amount of gap between the take-up frame sides 21, 22 holding them which allow the rollers to 30 and 40 to shift slightly to reduce the amount of chain twist.

As shown in FIG. 4 the rollers 30 and 40 are held between the frame sides 21, 22 through openings 24, 25 by threaded fasteners 19A, 19B with a small tubular bearing 18 that acts as the bearing in the openings 31, 41 of the sprockets 30, 40, respectively. Fastener 19A has a longer threaded end for securing the chain slack take-up idler arm 20 at the tapped opening 14. The shift cable 109 is to be attached in the hole or opening 15. As further shown the pivot guide feed arm 11 has a bent over portion 16 with a pivot hole 17 into which fits a tubular bearing sleeve 12A mounted on the pivot pin 12. A single spring 50 is shown that is connected at one end 51 to a bent over tab 19 at the bottom end of the pivot guide feed arm 11 and is further connected at an opposite end 52 onto a stop pin 26 on chain slack take-up idler arm 20.

In FIG. 5A and as is schematically shown in FIG. 10A (reversed looking from the opposite side), when a small sprocket 101S is selected, a long section of chain 60 must be stored in a back-and forth configuration adjacent to the derailleur sprocket nest 101. In FIG. 5B and schematically in FIG. 10B but similarly reversed, when a medium sprocket 101M is selected, the pivot guide feed arm angle allows the guide roller to drop and receive the chain in almost straight line from the drive sprocket 103.

A single spring 50 connected to the guide arm 11 and the chain slack take-up idler arm 20 supplies all the motion and take-up requirements for the system. When a chain 60 shift between small diameter sprockets 101S in the sprocket nest 101 is initiated, the chain 60 and the pivot guide feed arm 11 are moved sideways out of line with the top driving section of chain to avoid interfering between chain sections moving in opposite directions best shown in FIG. 9C.

Referring back to FIGS. 3B and 4, the pivot pin 12 is shown attached to a mounting bracket 13 which is to be attached by welding or otherwise fixed to the frame 110. The base of the bracket 13 aligns with the frame 110, and the pivot pin 12 is projecting at an angle to the inclined surface of the bracket 13. The inclined surface is oriented at an angle θ relative to the frame 110 as illustrated in FIGS. 9A, 9B, and 9C. The angle θ should be equal to the tangent slope of the sprocket nest 101, as shown in FIGS. 9A, 9B and 9C, the angle θ was 30 degrees. The angled pivot guide feed arm 11 fits over the pivot pin 12 and is rotatable about the pivot pin 12 while it translates back and forth to line up with the sprockets in the nest 101, and thus the pivot guide feed arm 11 rotates forward and translates sideways.

The pivot guide feed arm 11, as shown in FIG. 4, has a projecting tab 9 with a hole 15 for securing the gear shifting rod or wire 109. The tab 9 is located in close proximity to the pivot pin 12 to exactly duplicate the control wire motion of a conventional derailleur on bicycles. The pivot guide feed arm 11 is twisted about 30 degrees so that the orientation of the chain 60 passing through the guide rollers 30 and 40, shown as shallow toothed sprocket rollers, is substantially parallel to the drive sprockets and the rear sprockets of the nest 101, best shown in FIG. 9A.

Referring to FIGS. 10A, 10B and 10C, the single spring 50 connected near or at the pivot pin 12 provides torque through the chain slack take-up idler arm 20. When the chain 60 is on the major diameter rear sprocket 101L, the single spring 50 provided torque is modest but when the pivot guide feed arm 11 arm rotates to the smaller sprocket 101S, the single spring 50 is stretched but acts over a shorter distance to provide torque. This means as the derailleur 10 is shifted upward through the gears, the spring 50 assist in the movement of the derailleur assembly 10 and insures the slack in the chain 60 is fully taken out by the chain slack take-up idler arm 20.

Particular attention in FIG. 10C is called to the chain 60 when moved onto the smallest rear sprocket 101S. In this position, the derailleur 10 is orientated such that the chain 60 can encircle substantially more than 180 degrees around the sprocket 101S. As shown, almost 240 degrees of the smallest sprocket 101S is engaged by the chain 60. This feature is very beneficial in that the wrapping of the chain 60 enables more sprocket teeth to be engaged. In a conventional low hung derailleur, 180 degrees of engagement is the best to be hoped for. The device according to this present invention enables far more teeth to be engaged. This means that even a smaller sprocket diameter can be used increasing the range of gear ratios available in a single nest.

As further illustrated in FIG. 9B, the chain slack take-up idler arm 20 is modified such that the orientation is centered or aligned with the middle sprocket 101M, but as shown in FIGS. 9A and 9C, is slightly canted at either extreme major or minor diameter sprockets at the roller feed end F sprocket 30 and the idler I sprocket 40 of the chain slack take-up idler arm 20. This creates a slight twist in the chain 60, but because the guide rollers 30 and 40 have a gap or clearance when mounted in their respective frame sides 21, 22 in which they are held, they move laterally allowing the twist to straighten out relative to the sprocket to which it is attached. This along with the fact the single spring 50 provides less torque at both the top and the bottom of its range permits the chain 60 to straighten out. Conventional derailleurs use massive spring force and therefore require precise parallel alignment. The derailleur 10 according to the present invention is greatly simplified in its design and thus can easily accommodate this small amount of chain twist. This assumes of course the adequate distance is provided between centers of the forward drive sprocket 103 and the rear stacked sprocket nest 101, for example at least 10 inches, preferably 11 inches for a 0.5 inch bicycle chain and a six sprocket nest. This for a six speed derailleur allows a sufficient length of chain 60 to allow the twist angle to be small enough to straighten out due to the flexibility of standard bicycle chain.

A unique feature of this new derailleur design is that it can be used with a nested and stacked rear sprocket nest combined with a multiple forward drive sprocket nest and is capable of changing not only the rear gears, but the forward gears as well. Presently, two conventional derailleurs are required to develop adequate speed change on bicycles. The single spring tension of the present derailleur 10 of the present invention allows it to move the chain at both locations. While this has obvious cost benefits, it is believed the present inventions use of multiple forward sprockets is not providing the benefit for the cost required. This is true because of the duplication of gear ratios available means little or no real advantage is achieved.

A 27 speed derailleur system on a bicycle with rotating pedals actually provides about 8 distinct speeds with multiple redundant combinations requiring two sets of derailleur devices providing the intermediate speeds. The present invention derailleur 10 can provide a single location with a wider gear tooth range to equal the total gear ratio of a two derailleur bicycle system without the redundancy, reduced stress and wear of the multiple rear sprocket set and safer chain safety near the pedals.

The prior art has a 27 speed with a three sprocket nest at the pedal driving one of 9 rear wheel sprockets at the rear wheel derailleur positions providing duplicate intermediate speeds. The derailleur 10 of this invention offers a compact single control derailleur system without redundancy with equal step up ratios between speeds. This provides reduced stress and wear on the sprockets due to greater wrap around for small sprockets and greater safety near the pedals when a single chain location must be guarded instead of a 3 chain wide protected area.

The earlier described derailleur of FIGS. 2 through 5B has the normal tension spring action and stops on the pivot guide feed arm 11 to stop the pin 26 set to produce rotation of the pivot arm about a pivot limited less than 180 degrees rotation. When additional rotation is required, a hub projection 80 about or near the pivot can be located to rest against the spring coils and prevent or limit the tension spring coils from reaching the center of rotation of the pivot arm, as shown in FIG. 6. In this case one of the limit stops on the pivot guide feed arm 11 can be moved or eliminated. This effect was demonstrated on a scooter derailleur system. Wherein the correct selection of pivot projection in the shape of a cylindrical hub 80 with an appropriately sized cylinder diameter allowed the rotation to go well past the 180 degree rotation to well over 240 degrees represented as angle α. This increased rotation can be designed to fit the need.

This rotation over 180 degree for a pivot guide feed arm 11 with a single tension spring 50 drive provides several alternate configurations. The equivalence of the cylindrical hub 80 to develop over 180 degrees rotation of a spring return tension spring arm as shown in FIG. 6 can be achieved by lancing a segment 90 of sheet metal adjacent to the hub or pivot and form it to project outwardly and act as a guide supporting the spring 50 smoothly against the side coils of the tension spring, as shown in FIG. 7 represented by the angle β.

As shown in FIG. 8A, tension spring top swivel connector 86 may be built as a tube 86 with the ID swivel on a shaft or the pin 26 and the OD modified with a spring groove 88 to prevent the end twist loop of tension spring 50 from falling off the spring groove 88 at the spring contact area.

As shown, the entire derailleur assembly 10 can occupy and function between the space defined as a pair of tangent lines between major driven and major diameter nest sprockets. However, it is important to note the ground clearance needed simply requires the derailleur and take-up assembly to occupy a space between the horizontal tangent lines of the largest sprocket diameters.

Furthermore, as shown in FIGS. 9A, 9B and 9C the rear sprocket nest has a conical linear tangency shown as straight but preferably, can be made having a non-linear tangency or a curved peripheral profile. In such a case, the straight line angle formed between the largest sprocket and the smallest sprocket can be used to set the pivot pin angle. This means the distance between the derailleur feed sprocket 30 and the different sized sprockets will vary. This variation can be accommodated without detriment due to the sole requirement of feeding the chain 60 onto a specific sprocket.

It is understood that because the system moves along a fixed angle set by the pivot 12, the sweep angle of the derailleur 10 lies in a curved plane, accordingly the invention relies on a movement that uses this fact to set the appropriate variable distances between the derailleur guide feed roller sprocket 30 and the individual sprockets of the sprocket nest 101. Adjustment of these different aspects of the invention can be varied.

Variations in the present invention are possible in light of the description of it provided herein. While certain representative embodiments and details have been shown for the purpose of illustrating the subject invention, it will be apparent to those skilled in this art that various changes and modifications can be made therein without departing from the scope of the subject invention. It is, therefore, to be understood that changes can be made in the particular embodiments described which will be within the full intended scope of the invention as defined by the following appended claims. 

The invention claimed is:
 1. A derailleur for moving a chain to different sized sprockets arranged between a range of sizes increasing from smallest to largest in a sprocket nest, the derailleur comprises: an angled pivot guide feed arm for directing the chain onto one of multiple sprockets within the sprocket nest, wherein the angled pivot guide feed arm is rotatably mounted over pivot end on a single angular pivot pin fixed on an inclined surface attached to a frame, the inclined surface being oriented at an angle equal to a tangent slope of the sprocket nest as measured by a straight line formed between the largest sprocket and the smallest sprocket and when the angled pivot guide feed arm pivot end rotates about the pivot pin, an opposite upper chain guide end of the angled pivot guide feed arm supports a chain guide roller and traces a fixed planar arcuate path along a sweep angle set and controlled by the rotation about said singular angular pivot pin; a chain slack take-up idler arm having a pair of take-up frame sides, the chain slack take-up idler arm for chain slack take-up being pivotally connected to the upper chain guide end of the angled pivot guide feed arm and extending to a chain take up roller at a bottom opposite end of the chain slack take up idler arm, both the chain guide roller and the chain take-up rollers being held between the take-up frame sides of the chain slack take-up idler arm; and, wherein the angled guide feed arm and the pivotally connected chain slack take-up idler arm use the chain guide roller at the upper end to both direct the chain onto one of the sprockets and to take up chain slack at the chain slack idler arm, when the chain slack take-up idler arm is moved centered on a middle sprocket the chain guide roller and the chain take up roller are both aligned parallel and in the same plane with the middle sprocket of the sprocket nest wherein the chain slack take-up idler arm when moved from alignment with the middle sprocket is canted on an angle at either extremes of the smallest and largest sprockets wherein the chain guide roller and chain take-up roller are not aligned parallel and in the same plane relative to the respective smallest or largest sprocket creating a twist in the chain which is straightened out by a movement of the guide roller and chain take-up roller by utilizing a gap or clearance between the take-up frame sides of the chain slack idler arm.
 2. The derailleur of claim 1 wherein movement of the pivot guide feed arm is mechanically driven by a user command.
 3. The derailleur of claim 1 wherein the movement of the pivot guide feed arm is moved by a connected cable or rod or wire.
 4. The derailleur of claim 1 wherein the chain guide roller is a toothed roller.
 5. The derailleur of claim 1 wherein the angled pivot guide feed arm and chain slack take-up idler arm are both spring loaded by a single spring.
 6. The derailleur of claim 1 wherein the angled pivot guide feed arm and chain slack take-up idler arm share a single spring, the single spring being connected to the pivotal guide feed arm and the chain slack take-up idler arm.
 7. The derailleur of claim 6 wherein the spring biases both the pivot guide feed arm and chain slack take-up idler arm.
 8. The derailleur of claim 7 wherein one end of the spring is connected to the angled pivot guide feed arm near the pivot end and the opposite end of the spring is connected to the chain slack take-up idler arm biasing the chain slack take-up idler arm to provide the chain slack take-up.
 9. The derailleur of claim 1 wherein the chain slack take-up idler arm lies within a space between the driver sprocket and driven sprocket nest, the space defined as the area between the major diameter sprocket of the driver sprocket and driven sprockets wherein the entire derailleur is located in the space defined by an upper line and a lower line drawn between the major diameters of the largest or major sprocket of the sprocket nest and the major diameter of the forward drive sprocket.
 10. The derailleur of claim 1 wherein a distance of at least 10 inches is provided between the drive sprocket and the driven sprocket nest.
 11. The derailleur of claim 1 wherein the nested and stacked rear sprocket nest having multiple sprocket gears is combined with a multiple forward drive sprocket nest having multiple sprocket gears and the derailleur is capable of changing both the rear gears and the forward gears by moving the chain at both locations using the one derailleur.
 12. A derailleur for moving a chain to different sized sprockets arranged between a range of sizes increasing from smallest to largest in a sprocket nest, the derailleur comprises: an angled pivot guide feed arm supporting a chain guide roller for directing the chain onto one of multiple sprockets within the sprocket nest, wherein the angled pivot guide feed arm is rotatably mounted over pivot end on a single angular pivot pin fixed on an inclined surface attached to the frame, the inclined surface being oriented at an angle equal to a tangent slope of the sprocket nest as measured by a straight line formed between the largest sprocket and the smallest sprocket and when the angled pivot guide feed arm pivot end rotates about the pivot pin, an opposite upper chain guide end supporting the chain guide roller of the pivot guide feed arm traces a planar arcuate path along a sweep angle set and controlled by the rotation about said singular angular pivot pin; a projection about or near the pivot end, wherein coils of a tension spring rest on the projection and prevent or limit the tension spring coils from reaching the center of rotation and the tension spring biases both the angled pivot guide feed arm and a chain slack take up idler arm having a chain take up roller and a pair of take-up frame sides, the tension spring being connected to the angled pivotal guide feed arm and the chain slack take-up idler arm, both the guide roller and the chain take-up rollers being held between the take up frame sides of the chain slack take-up idler arm; and wherein when the chain slack take-up idler arm is moved centered on a middle sprocket the chain guide roller and the chain take up roller are both aligned parallel and in the same plane with the middle sprocket of the sprocket nest wherein the chain slack take-up idler arm when moved from alignment with the middle sprocket is canted on an angle at either extremes of the smallest and largest sprockets wherein the chain guide roller and chain take-up roller are not aligned parallel and in the same plane relative to the respective smallest or largest sprocket creating a twist in the chain which is straightened out by a movement of the guide roller and chain take-up roller by utilizing a gap or clearance between the take-up frame sides of the chain slack idler arm.
 13. A derailleur for moving a chain to different sized sprockets arranged between a range of sizes increasing from smallest to largest in a sprocket nest, the derailleur comprises: an angled pivot guide feed arm bent supporting a chain guide roller for directing the chain onto one of multiple sprockets within the sprocket nest, wherein the angled pivot guide feed arm is rotatably mounted over pivot end on a single angular pivot pin fixed on a frame or on an inclined surface attached to the frame, the inclined surface being oriented at an angle equal to the tangent slope of the sprocket nest as measured by a straight line formed between the largest sprocket and the smallest sprocket and when the angled pivot guide feed arm pivot end rotates about the pivot pin, an opposite upper chain guide end supporting the chain guide roller of the pivot guide feed arm traces a fixed planar arcuate path along a sweep angle set and controlled by the rotation about said singular angular pivot pin; a single tension spring biasing the pivot guide feed arm, the tension spring being connected to the twisted pivot guide feed arm at or near the pivot end and to a chain slack take-up idler arm having a chain take up roller; a lancing segment of sheet metal adjacent a hub or pivot to support the tension spring smoothly against the side coils of the spring; and wherein when the chain slack take-up idler arm is moved centered on a middle sprocket the chain guide roller and the chain take up roller are both aligned parallel and in the same plane with the middle sprocket of the sprocket nest wherein the chain slack take-up idler arm when moved from alignment with the middle sprocket is canted on an angle at either extremes of the smallest and largest sprockets wherein the chain guide roller and chain take-up roller are not aligned parallel and in the same plane relative to the respective smallest or largest sprocket creating a twist in the chain which is straightened out by the movement of the guide roller and chain take-up roller by utilizing a gap or clearance between the take-up frame sides of the chain slack idler arm.
 14. The derailleur of claim 13 further comprises: a tension spring swivel connector built as a tube or pin to prevent an end loop of the spring from falling off. 